Hydraulic screw feed



Aug. 17, 1954 Filed July 3l, 1950 l.. A. LEIFER ET AL' HYDRAULIC SCREW FEED sheets-sheet 1 INVENTORS L0r@nZA.Le zfer ewis W Premo ATTORNEYS Aug- 17, 1954 l.. A. LEIFER ETAL 2,685,448

HYDRAULIC SCREW FEED Filed July 3l,` 1950 3 Sheets-Sheet 2 ATTORNEYS ug 17, 1954 L. A. LEIFER Erm.

HYDRAULIC SCREW FEED Filed July 51, 1950 1| :a ml? x @Cf im g QA usan? n L'iz i @n f HIV n.; la 5% f 'V\ O 7 ai, o/ Q 1| y 5m r/ /lggv *FF- .g f- Us i? C Tf'- J J (n 3 Sheets-Sheet 3 INVENTORS LorenzA. Lez er ATTORNEYS.

Patented Aug. 17, 1954 HYDRAULIC SCREW FEED Lorenz Albert Leifer and Lewis W. Premo, Madison, Wis., assignors to Gisholt Machine Company, Madison, Wis., a corporation of Wisconsin Application July 31, 1950, Serial No. 176,894

10 Claims. 1

This invention relates to a hydraulic-screw feed and has found application in the accurate feeding of cutting tools on lathes and the like.

One of the principal objects of the invention is to provide a hydraulically powered lead screw and to thereby utilize the infinite variations in speed possible with hydraulic controls.

Another object of the invention is to provide a more accurate slide feed with a lead screw.

Another object is to provide a very fine adjustment for depth of cut with a lead screw.

Another object is to provide a very accurate, sensitive and effective stop for the lead screw.

Another object is to provide a hydraulic lead screw mechanism wherein a relatively large volume of operating fluid is employed, thereby minimizing the effect of fluid leakage.

Another object is to provide a hydraulic lead screw mechanism wherein a relatively low iiuid pressure is employed and is multiplied in power to thereby minimize the eiects of temperature changes and the like.

Another object is to provide a rapid traverse operation for the lead screw without interfering with the accurate lead screw feed control.

Another object is to provide an attachment which may be applied to any machine tool for effecting feeding operations.

Other objects and advantages of the invention will appear hereinafter in connection with the description of an application of the invention to the tool slide feed of a lathe, as illustrated in the accompanying drawings.

In the drawings:

Figure 1 is a perspective view of a portion of a lathe showing a tool-slide and the hydraulic lead. screw feed therefor in the form of an attachment;

Fig. 2 is a front elevation of the slide and the lead screw attachment;

Fig. 3 is a top plan View of the slide and lead screw attachment;

Fig. 4 is an enlarged longitudinal section taken centrally of the lead screw and of the power cylinder showing the parts prior to the commencement of a feeding operation;

Fig. 5 is a similar view showing the parts at the instant of completion of the cut and with a schematic view of the hydraulic power circuit; and

Fig. 6 is an enlarged transverse section taken longitudinally of the cross shaft on line 6-6 of Fig. 3.

In carrying out the invention the lead screw is held against rotation and a. nut thereon is driven byv a hydraulic cylinder and piston through an intermediate rack and worm gear providing a substantial power ratio, the nut being mounted to provide feed and traverse thrust to the tool slide. Quick traverse is provided by a direct hydraulic thrust movement of the lead screw. A micrometer-type adjustment is obtained between the drive piston and the rack mounted thereon for fine adjustment of the depth of cut. A similar coarse adjustment is provided between the nut and lead screw to determine the position of the traverse movement.

When the invention is employed on a lathe the hydraulic drive is correlated to the spindle rotation and automatic pressure trip valves are employed to provide the desired sequence of movements which normally include forward traverse, forward feed, and back traverse to starting position. Both traverse movements preferably include a quick traverse which in the case of back traverse quickly withdraws the tool from the work.

The invention has been embodied in an attachment applicable to various machine tools, and is illustrated as applied to a lathe I having a bed 2, a headstock 3 and a tailstock 4.

The headstock 3 of the lathe has the rotary spindle 5 driven by means of suitable clutches and transmission gearing within the headstock from the electric drive motor 6 mounted on the rear o-f the same.

The tool feed attachment 1 is mounted on the bed 2 on the rear side and comprises a base 3 bolted to the top of the bed and providing ways 9 for the tool-cross-slide It.

The base 8 carries a pair of power cylinders I I and I2 disposed between the ways 9 and parallel thereto.

The slide I 0 has a flat top and downwardly depending side flanges constituting a cover for the base and which provide tapered gibs I3 matching the ways 9 for guiding the slide I in its movement toward and away from the work.

The slide I0 has a pair of T-slots I4 in its upper surface for adjustably mounting a tool block I5 carrying the cutting tool I6.

The power cylinder I I is a sho-rt stroke traverse cylinder having a piston I7 and. piston rod I8, which for all practical purposes of operation of cylinder I I, may be considered directly connected to slide I. In previous hydraulic cross-slide or tool-slide feeds it was customary to utilize such a direct connected power cylinder for all traverse and feed purposes, with the result thatit was necessary to employ high-duid pressure and Very secured against rotation by set screw 2|. The

lead screw I9 carries a rotary nut Y22 threaded thereon and which in turn is mounted for rotation in a cylindrical housing 23 constituting an outward extension of the slide i0.

The nut 22 consists of a sleeve'made upof two aligned cylindrical parts having a parting line centrally of the threaded section and which are constructed to be secured'together by bolts 24 which provide for axial adjustment of the sleeve parts so that the flank .of the threads of one part engage the threads of lead screw I9 on one side of the threads while the flank ofthe threads of the other part engage the threads of the lead screw I 9 on the opposite side, thereby adjustably eliminating backlash between the nut 22 and lead screw I9.

The nut 22 kis constructed to transmit axial thrust forces to slide I by means of the roller thrust bearings 25 and 2S disposed on opposite sides of an internal flange 2l of housing 23.

Bearing 25 abuts flange 27 on its inner side and a shoulder 28 of nut 22 on its outer side. Bearing 26 abuts nange 21 on its outer side and a nut' 29, secured on the inner sleeve-like end of nut 22. The nut 29 serves to eliminate play in the thrust bearings 25 and 26 whereby an accurate control ofthe movement of slide l0 by nut 22 is provided at all times.

The nut'22 is rotationally driven by a gear 30 keyed on the outer end thereof and held to move axially therewith by means of a pair of guide bushings 3i and 32 for nut 22 in the outer end of housing 23.

The gear 33 is driven by a complemental worm gear 433 meshing therewith and mounted on a cross shaft 3l: mounted rfor rotation in suitable bearings in an adjacent part of housing 23.

A spurgear 35 on the other end of shaft 34 meshes with a drive rack 36 on a sleeve 21 carried by a piston rod 38-whose pistonv 35i operates in power cylinder l2..

The feed of slide l0 is eiected by the rotational threading of nut 22 upon lead vscrew i9 by reason of the movement of piston 39 in cylinder i2 and the consequent movement of rack 35 rotating gear 35, shaft 3d and worm gear 33 and in turn gear on nut 22.

The feed drive described provides a substantial speed reduction and mechanical advantage in feeding the slide iii. trated, the ratio is 20 to 1, i. e. lthe axial movement of piston 39 is twenty times that of nut 22 and slide l0, thereby providing a very substantial power advantage.

Invaddition to the power advantage described, it is possible to construction piston 39 with a substantial area so that low pressures may be employed for the hydraulic system, thereby reducing the'leakage and taking advantage of the fact that it is kgenerally easier to'provide a large volume of oil flow at a lower pressure than tc provide a small volume at a high pressure; A low pressure large volume system has less variablencss In the construction illusdue to leakage and due to temperature changes that might effect changes in oil volume and in conduit sizes.

In the attachment illustrated an oil pressure of one hundred pounds per square inch lbs. p. s. i.) will produce a thrust force inwardly on a ten-square-inch piston 39 of one thousand pounds (1,000 lbs.) which is multiplied to a thrust force of twenty thousand pounds (20,000 lbs.) on the cutting tool I6.

A coarse and fine adjustment is provided which effects a very accurate control of the depth of cut. For this purpose the coarse adjustment is obtained by releasing set screw 2| and threading leadv screw i9 -either inwardly or outwardly of nut 22 by applying a suitable wrench to the outer end of the lead screw. A complete revolution of lead screw IS relative to nut 22 will provide an axial adjustment equal to the pitch of the thread therebetween, which, in the embodiment illustrated is approximately one-quarter ofY an inch (MU). A scale 40 in a head il on the outer end of nut 22 4serves to indicate similar adjustments corresponding to one one-hundredth of an inch (.01.)'.

The scaleill constitutes graduations in the face of a conical surface exposed in a window 42 in head Hand whichare matched by corresponding graduations on a Vconical surface of a Banged sleeve :i3 keyed to the lead screwl, the flange on sleeve 43 rotating within head 4l and having its scale graduations exposed through the window 42.

The turning of lead screw'lg by a wrench applied to its outer end effects relative movements justment for the feed and is actually superimposed upon the coarse adjustment described above.

The ne adjustment is provided by employing sleeve member 3'! through which piston rod 33 is threaded', so that the position of rack 36 upon the piston rod 38 may be adjusted by turning the latter by a wrench applied toi the outer vend of the piston rod. For that purpose, sleeve 37 is keyed to housing 23 to prevent turning of the sleeve.

The stop is provided by a collar fili rmly attached on the piston rod 38 engaging the race i5 of the base 8 at the head of cylinder l2 and thereby determining the feeding movement. The.

longitudinal position of rack 36 on piston rod 38 determines the position of cutting tool I6 at the time stop collar ifi engages face 45 ofbase 8.

The adjustment for the position of rack 36 on piston -rod 38 in relation to stop collar lll is calibrated on a scale 26 comprising graduations marked around the circumference of a dial member 41 secured by a set screw 48 to the outer end of piston `rod 38 and encircling the outer end of the sleeve member 3? carrying rack 36. The set screw i9 normally securing piston rod 38 from turning relative to sleeve 3'1 should be released' distance of two one-thousandths of an inch (.002) and vthe intermediate short: graduation on; scale 146 representsra .distance yofonehone thousandth of an inch (.001") in relative movement between rack and stop collar 44.

Since the movement of tool I6 is only onetwentieth that of rack 36 in operation of the drive, the adjustments described above for scale provide a one-ten-thousandth of an inch v(.0G9l") adjustment in depth of cut of tool l5 for each long graduation on the scale, and a onehalf ten-thousandth of an inch (.00005") adjustment in depth of cut of tool l5 for each intermediate short graduation on the scale.

Since the piston 35 has to move twenty times as far as the cutting tool l5 in the illustrated embodiment described, the maximum possible length of feed for tool i5 is one-twentieth of the maximum operative length of movement of piston 39 in cylinder l2 having regard to the stop collar lili.

The hydraulic system for operating pistons il and 39 comprises a sump 5t, with three conduits or passages 5|, 52 and 55, respectively, leading to the master control valve 5d from which conduit 55 leads to the right hand or outer ends of both cylinders l l and I2, and a conduit 55 leads to the left hand or inner ends of both cylinders l I and l2.

The passage 52, illustrated as the central passage in Fig. 5 contains the main supply pump 57, often referred to as the traverse pump. A branch passage 58 leads from the passage 52 at the discharge side of pump 5l to passage 5l.

In line 5i, between the connection of passage r S with passage 5i and the sump 50 there is a `pressure relief valve 58 which regulates the fluid pressure supplied by the main pump 51. In line 5l, between the connection of passage 58 with passage 5| and the master control valve 55 there is a feed pump 55 which is designed to raise the 'pressure for a relatively small quantity of fluid to effect a power feed for the tools.

The line 53 constitutes a return line from valve 51! to the sump 5B.

The valve 55 is of any suitable automatic hydraulic valve construction wherein a plunger is made to shift automatically to successive positions by pressure surges in the power line. A manual control lever 5i on the valve serves to initiate each cycle of operation.

in operation, after the starting movement of lever 5 i, and with the parts in the position shown in Fig. 4, the master control valve 545 admits pressure fluid from both the traverse pump 5l and the feed pump 55 through conduit 55 to the outer end of both cylinders I l and i2, thereby forcing both pistons il and 35 inwardly at the same time and moving the entire slide lll inwardly at a quick traverse rate.

The oil in the inner end of cylinder l I is forced by piston il to escape through a branch passage 52 of conduit 55, and from thence through valve 515 to the return line 53 and sump 50.

The oil in the inner end of cylinder l2 is forced by piston Se to escape through pilot port 63 into conduit 55, and from thence through valve 54 to the return line 53 and sump 55.

When piston i1 reaches its extreme inward position as in Fig. 5 the traverse fluid continues to move piston 59 inwardly at a traverse rate, thereby operating rack 35 and effecting rotation of nut 22 which in turn compels continued movement of slide i il inwardly at a traverse rate until the tools reach the initial cut location, whereupon pilot plug 5 enters port $3 closing the same.

When port 63 is closed, as described above, the discharge fluid from the inner end of cylinder `l2 .flows through a by-pass passage 65 having a ball check valve 65 therein which is normally open to the ow of fluid at feed rates but which is forced to close when the traverse flow is imposed therethrough.

Closing of valve 66, as described above, bars further inward movement of piston 39 and results in a pressure surge or impulse being transmitted back through the driving fluid to the master control valve 54, effecting a shifting of the latter to a position wherein passage 52 is closed and fluid is supplied to the outer end of cylinder l2 only from feed pump in passage 5i.

The momentary shutting off of pressure fluid from cylinder l2 during shifting of valve 55 permits ball check valve to drop to open position. Thereafter a forward feed 0f piston 59 is effected by power fluid from feed pump 5i! at a rate which does not compel closing of Valve 55.

The feed of slide l) and tool I5 continues until stop collar 4@ engages stop surface i5, whereupon the movement of piston 39 is terminated and a pressure surge or impulse is transmitted back through the driving fluid to valve 54, shifting the latter to a back traverse position.

In the back traverse position valve 54 transmits power fluid from both pumps 5l and Bil in lines .52 and 5l respectively, through conduit 55 to the inner ends of both cylinders li and I2 thereby forcing pistons il and 59 outwardly together. The piston Il thereupon moves outwardly its full stroke in cylinder l l giving a quick back traverse to slide lil effecting an initial rapid Withdrawal of tool l 5 from the Work. After piston il reaches the outer end of cylinder il, traverse movement of slide i8 continues by a traverse outward movement of piston 39 in cylinder i2, rotating nut 22 to effect the same. When piston 3s reaches the outer end of cylinder i2 its movement terminates and a pressure surge or impulse is transmitted back through the conduit 55 to master control valve 55 shifting the latter to a shut-olf position. The oil in cylinders il and I2 will retain pistons Il and 59 in their outermost positions until the lever 5l is again moved to open the valve 55 and start a cycle.

The operator utilizes the time involved in traversing rack 36 outwardly to start position in which to unload and load the machine.

The invention provides a very smooth feed capable of adjustment to as low as one-half a tenthousandths of an inch (.GS005") per revolution of the spindle 5.

The slide movement is so accurate that repeated operation over many cycles will retain extremely close tolerances in depth of out.

lThe fast coarse adjustment is of particular advantage when changing from and to various sizes of work.

The fine adjustment gives excellent accuracy of operation.

The large fluid volume employed during feeding is of considerable advantage in effecting a quick rise in pressure upon engagement of stop collar M with face :i5 and a reversing of valve 54 in only a small fraction of a revolution of spindle 5.

The invention avoids errors previously encountered in hydraulic drives for slides since the lead screw protects the pressure iluid against changes caused by variations or differences in tool hardness and cutting conditions. Consequently, the pressure engagement between stop collar lill and face 55 will be much alike for each cycle of .operation and there vwill be very little tolerance variation 'due to possible changes of stop pressures.

Furthermore, any variation in stop pressures will hardly eiiect the tool position at all, since the ratio of movement of stop collar lll to the movement of the tool is high, i. e. of the order of twenty to 1 (20:1) in the embodiment illustrated. This high ratio of movement between the stop and the tool greatly increases the accuracy of the cut.

The quick traverse provided by cylinder l l and piston l1 may be eliminated where the ordinary traverse and feed of cylinder l2 and piston 3Q is satisfactory. Where the quick traverse is employed and it is desired to obtain the full advantage of the previously described 26,0518 pounds pressure feed on the tool, a high pressure fluid supply should be provided to cylinder li separate from and instead of the supply from line 55, or in lieu thereof some means of securing the piston il against back thrust movement.

The invention may be employed in various types of machines, and for almost any use wherein it is desired to control a hydraulic feeding movement to an accurate stop position.

Various embodiments of the invention may be employed within the scope of the following claims.

l claim:

l. ln a device of the class described for feeding a tool slide, feed screw and nut elements assembled in threaded relation to each other and disposed to eiect feeding of the tool slide by relative axial movement between the elements resulting from relative rotation, means normally securing one of said elements against rotation while leaving the other free to rotate, means normally securing one of said threaded elements against axial movement while leaving the other free to move axially under threadingr engagement therewith, thrust means to transmit movement to the slide from said axially movable threaded element, a hydraulic power cylinder member having' a piston member therein disposed to be relatively moved axially by means of power liquid flow into a corresponding end of the cylinder member, means to secure one of said members against axial movement while leaving the other member free to move axially, a gear rack on said axially movable member, a gear on said rotational element, an intermediate gear drive carried by the slide and connecting said rack and said gear whereby the feed of the tool slide is effected by a substantially large volume of iiow of low-pressure power liquid into the cylinder member to move one of said cylinder and piston members axially and actuate the gear driving the rotational element through operation of the rack and gear drive by said axial movement of said member, and means to effect a quick traverse movement of the slide by moving said feed screw and nut bodily axially, said rack being disposed parallel to said traverse and feed movements whereby said intermediate gear drive moves along said rack during the traverse and feed movements described.

2. ln a device of the class described for feeding a tool slide, lead screw and nut elements assembled in threaded relation to each other and disposed to eilect feeding of the tool slide by relative axial movement between the elements resulting from relative rotation, means normally securing one of said elements against rotation while leaving the other free to rotate, means normally securing one of said threaded elements against axial movement while leaving the other free to move axially under threading engagement therewith, thrust means to transmit movement to the slide from said axially movable threaded element, a hydraulic power cylinder member having a piston member therein disposed to be relatively moved axially by means of power liquid ilow into a corresponding end of the cylinder member, means to secure one of said members against axial movement while leaving the other member free to move axially, a gear rack on said axially movable member, a gear on said rotational element, an intermediate gear drive carried by the slide and connecting said rack and said gear and providing a substantial mechanical advantage between said hydraulic power drive said lead screw feed whereby the feed is effected by a substantially large volume of flow of low-pressure power liquid into the cylinder member to move one of said cylinder and piston members axially and actuate the gear driving the rotational element through operation of the rack and gear drive by said axial movement of said member, a stopl between said cylinder and piston members to limit the feeding movement of the slide with the mechanical advantage enhancing the accuracy of the nal feed position, and means to adjust the axial position of said rack upon said axially movable member in line increments whereby said mechanical advantage efects a correspondingly ne adjustment or the slide feed termination by said stop.

ln a device of the class described for feeding a tool slide, lead screw and nut elements assemled in threaded relation to each other and disposed to effect feeding of the tool slide by relative movement between the elements resulting from relative rotation, means normally securing one of said elements against rotation while lea-ving the other free to rotate, means normally securing one of said threaded elements against axial movement while leaving the other free to move axially under threading engagement therewith, thrust means to transmit movement to the slide from said axially movable threaded element, a hydraulic power cylinder member having a piston member therein disposed to be relatively moved axially by means of power liquid ow into a corresponding end of the cylinder member, means to secure one of said members against axial movement while leaving the other member free to move axially, a sleeve threaded onto said axially movable member and having a gear rack thereon, means normally preventing threading adjustment between said sleeve and axially movable member, a gear on said axially movable rotational element to drive the same, an intermediate gear drive carried by the slide and connecting said rack and gear whereby the feed of the tool slide is effected by a substantially large volume flow of low-pressure power liquid into the cylinder member to move one of said cylinder and piston members axially and actua-te the gear driving the rotational element through operation of the rack and gear drive by said axial movement of said member, a stop between said cylinder and piston members to limit the feeding movement of the slide, means to effect threading adjustment between said sleeve and axially movable member to accurately predetermine the iinal feed position, and means to provide an adjusted zone of feeding movement of the slide by effecting an adjusting rotation of said normally non-rotatable element relative to said rotational element.

fl. In a lathe, a tool slide, a support for said slide, a pair of hydraulic cylinders disposed side by side in said support, pistons operable in said cylinders, one of said pistons having a threaded rod and the other having a rod with a longitudinal gear rack thereon, said rods extending side by side axially from the corresponding cylinders, a housing for said rods carried by said slide, a nut on said threaded rod disposed with thrust bearings operably engaging an abutment within said housing and moving the same and said slide with axial movement of the nut, and a gear drive carried by said housing and connecting said rack and nut to effect rotation of the latter upon movement of the piston carrying said rack relative to the other piston, both of said cylinders cooperating to effect traverse movement of said slide, and said last named piston effecting slide feed.

5. In a lathe, a tool slide, a support for said slide, a hydraulic cylinder in said support, a piston operable in said cylinder and having a piston rod extending outwardly of the cylinder, an extension carried by said slide and housing said rod, a gear rack on said piston rod, a lead screw carried by said support and extending parallel to said piston rod in said slide extension, a feed nut threaded upon said lead screw and having thrust engagement with an abutment within said slide extension, means to secure one of said two last named elements against rotation, a gear drive carried by said slide extension between said rack and the other of said named elements to rotate the latter and effect movement of said slide in response to movement of said piston, and means within said support to move said lead screw anl nut axially bodily with said slide and slide extension, and rack and piston for a predetermined traverse distance for the slide.

6. A lathe attachment comprising, a tool slide, a support for said slide adapted to be secured by a lathe bed, a pair of hydraulic cylinders disposed side by side in said support, pistons operable in said cylinders, one of said pistons having a threaded rod and the other having a rod with a longitudinal gear rack thereon, said rods extending side by side axially from the corresponding cylinders, a housing for said rods carried by said slide, a nut on said threaded rod disposed with thrust bearings operably engaging an abutment within said housing and moving the same and said slide with axial movement of the nut, a gear meshing with said rack and secured to a cross shaft carried by said housing and extending adjacent and laterally of said rods, and a worm gear on said shaft meshing with a worm gear on said nut to drive the latter, both of said cylinders cooperating to effect traverse movement of said slide, and said last named piston effecting slide feed.

7. In a lathe, a tool slide, a support for said slide, a pair of hydraulic cylinders disposed side by side in said support, pistons operable in said cylinders, one of said pistons having a threaded rod and the other having a rod with a longitudinal gear rack thereon, a slide extension housing said piston rods, a nut on said threaded rod disposed with thrust bearings operably engaging an abutment within said slide extension and moving the same with axial movement of the nut, a gear drive carried by said slide extension and connecting said rack and nut to effect rotation of the latter upon movement of the piston carrying said rack relative to the other piston, and a stop on the piston rod carrying said rack disposed to enga-ge a corresponding stop on said slide support to effect a termination for the tool out, both of said cylinders cooperating to effect traverse movement of said slide, and said last named piston effecting slide feed.

8. In a lathe, a tool slide, a support for said slide, a pair of hydraulic cylinders disposed side by side in said support, pistons operable in said cylinders, one of said pistons having a threaded rod and the other having a rod with a longitudinal gear rack thereon, a nut on said threaded rod disposed with thrust bearings operably engaging said slide and moving the same with axial movement of the nut, a gear drive between said rack and nut to effect rotation of the latter upon movement of the piston carrying said rack relative to the other piston, a stop on the piston rod carrying said rack disposed to engage a corresponding stop on said slide support to effect a termination for the tool out, and means to adjust the axial position of said rack upon the piston rod carrying the same to effect a fine adjustment for termination of the tool cut by said stop, both of said cylinders cooperating to effect traverse movement of said slide, and said last named piston effecting slide feed.

9. In a lathe, a tool slide, a support for said slide, a pair of hydraulic cylinders disposed side by side in said support, pistons operable in said cylinders, one of said pistons having a threaded rod and the other having a rod with a longitudinal gear rack thereon, a nut on said threaded rod disposed with thrust bearings operably engaging said slide and moving the same with axial movement of the nut, a gear drive between said rack and nut to effect rotation of the latter upon movement of the piston carrying said rack relative to the other piston, a stop on the piston rod carrying said rack disposed to engage a corresponding stop on said slide support to effect a termination for the tool out, means to adjust the axial position of said rack upon the piston rod carrying the same to effect a ne adjustment for termination of the tool cut by said stop, and means to adjust the axial position of said nut relative to the piston rod carrying the same to effect a coarse adjustment for the traverse movement and for termination of the tool cut by said stop, both of said cylinders cooperating to effect traverse movement of said slide, and said last named piston effecting slide feed.

1-0. In a lathe, a tool slide, a support for said Islide, a pair of hydraulic cylinders disposed side by side in said support, pistons operable in said cylinders, one of said pistons having a threaded rod and the other having a rod with a longitudinal gear rack thereon, a nut on said threaded rod disposed with thrust bearings operably engaging said slide and moving the same with axial movement of the nut, a gear drive between said rack and nut to effect rotation of the latter upon movement of the piston carrying said rack relative to the other piston, a stop on the piston rod carrying said rack disposed to engage a corresponding stop on said slide support to effect a termination for the tool cut, means to adjust the axial position of said rack upon the piston rod carrying the same to effect a fine adjustment for termination of the tool out by said stop, means to adjust the axial position of said nut relative to the piston rod carrying the same to effect a coarse adjustment for the traverse movement and for termination of the tool cut by said stop, and means to supply power liquid to said cylinders in correlation to effect a cutting cycle which includes an initial quick forward traverse, a short intermediate forward traverse, a forward feed to stop position, an initial quick back trav-` erse and a nal back traverse which resets the feed screw for the next cycle.

References Cited in the le of this patent UNITED STATES PATENTS Number Name Date McGowan Sept. 7, 1886 Taylor May 27, 1890 Vaughan Nov. 14, 1905 CarsonV Feb. 1, 1921 Smith Feb. 28, 1928 Number` Number Name Date Smith Feb. 28, 1928 Haas Oct. 9, 1934 Price Mar. 14, 1939 Snader July 4, 1944 Casella July 9, 1946 Bullard June 21, 1949 Casella Aug. 14, 1951 FOREIGN PATENTS Country Date Great Britain Dec. 10, 1929 

